A7 B7 五、發明説明（i ) 本發明有關利用不同冷凌逾丨占、 使用之r…系，以在持續長期 範園下及/或蒸汽注入該壓縮機時提供改善之效 ’俾能於加熱及冷卻模式二者中増加容量及效率。 熱泵系統通常係爲雙向的，亦即其可提供加熱或冷卻， 或有時候同時提供兩者。吾人已知利用多重成份之CFC或 HCFC冷滚劑以當用於加熱時延伸該熱系有效範圍之低溫端 。然而’近來由於能促成地球臭氧層之耗竭及全球溫室效 應又氣含量而在使用CFC，S或HCFC，s之限制，現在已轉變 至強調使用HFC，s及其他可爲環境所接受之冷凍劑。現行 供電住宅用及小型商業用熱泵系統具有二種操作及性能限 制。主要是其在低於約華氏3〇度或華氏4〇度以下之周遭溫 度時具有不足之容量，以致必得，利用諸如電阻加熱或礦物 燃料燃燒之輔助式熱源。此外，藉著在低周遭溫度下運轉. I熱泵對空氣所能加熱之溫度爲人類之舒適感而言仍太低 約低於華氏90度之空氣進入一房間時由於該空氣之流動 而提供一刺骨風寒之不舒適感。 本發明之目的包含提供一具有很寬廣之周遭溫度操作範 圍之熱泵系統，該熱泵系統在該寬廣之周遭溫度範園内有 效率地操作，而符合建築物之加熱負載需求，藉著在一充 分尚溫下有效率地提供空間對流加熱空氣以提供舒適之室 内空氣運送溫度，以致不會造成一寒冷氣流效果，及利用 環境可接受、安全之冷凍劑。其他目的包含増加一設有給 定壓縮機之熱泵系統之容量及效率。 根據本發明之第一論點，一熱泵系統採用含有比該混合 本紙張尺度適用中國國家標準（CNS ) Λ4規掐（210X297公# ) s衣-- (請先閱讀背面之注意事項再填寫本頁) -訂 經濟部中央標隼苟員工宵玢合乍‘土 泛 經濟部中央標準局貝工消費合阼"午輟 A7 ___________B7 ' 五、發明説明（2 ) — _ 物之其他成份具有較高沸點之一或多種成份之多成份非 刺激性（zeotropic)混合冷凍劑，利用足以滿足系統容量而具 有由該混合物分開之一實質部份低壓成份之許多冷凍劑， 及一由精餾塔及分離器所進給以由該系統混合物除去低壓 成份之儲存槽。根據本發明之另一論點，可加熱該儲存槽 中之流體以進一步増加該低壓成份由該混合物之分離。又 根據本發明之論點，當該系統正在該加熱模式下操作時， 可用該凝結器之流出物加熱該儲存槽流體，藉此使該返回 冷凍劑過冷。當該低壓成份實質上已由該系統混合物移去 及存在該儲存槽時，其可能隔離及不需要繼續該精餾製程 或冷凍劑之任何特別加熱或冷卻v或在該加熱模式下之整 個操作時期中可繼續該精餾製程。本發明之論點在極多 HFC混合物及其他環境可接受之冷凍劑下運作完美。—種 提供R407C之此類冷凍劑因其R32, R125&R134a之含量而運 作特佳。目前之成份包括R32(百分之23)、Rl25(百分之25) 及R134a(低壓成份）爲百分之52。然而，該冷凍劑及其他 HFC's之各種結合亦將有效率地運作。 根據本發明之另一級内壓縮論點，冷凍劑之蒸汽係在一 選定壓力下於平衡溫度中由該系統冷凍劑流動分開，該平 衡溫度係在凝結器流出物溫度及該蒸發器流出物溫度之間 ，然後該蒸汽實質上在該選定受壓點於其壓縮衝程中進入 孩壓縮機。按照本發明之論點，用一灌水槽或藉由在該冷 凉劑流動之液體及蒸汽成份之間提供熱交換以完成蒸汽分 離。本發明之論點對任何給定壓縮機之熱泵系統提供增加 -5- 獻度適用中國國家:-- I I I I I--- (請先閱讀背面之注意事項再填寫本頁)A7 B7 V. Description of the invention (i) The present invention relates to the use of different cold lings to occupy and use r ... to provide improved effects under continuous long-term conditions and / or when steam is injected into the compressor. Increased capacity and efficiency in both heating and cooling modes. Heat pump systems are usually bi-directional, that is, they can provide heating or cooling, or sometimes both. We know the use of multi-component CFC or HCFC cold rolling agents to extend the low temperature end of the effective range of the thermal system when used for heating. However, recently, the restrictions on the use of CFC, S or HCFC, s due to the depletion of the earth's ozone layer and the global greenhouse effect and gas content have now shifted to the emphasis on the use of HFC, s and other environmentally acceptable refrigerants. Existing power supply residential and small commercial heat pump systems have two operational and performance limitations. Mainly it has insufficient capacity at ambient temperatures below about 30 degrees Fahrenheit or below 40 degrees Fahrenheit, so that it is necessary to use auxiliary heat sources such as resistance heating or fossil fuel combustion. In addition, by operating at low ambient temperatures. I The heat pump is still too low for human comfort to heat the air. The air below 90 degrees Fahrenheit provides a The uncomfortable feeling of bitter cold. It is an object of the present invention to provide a heat pump system with a wide ambient temperature operating range. The heat pump system operates efficiently in the wide ambient temperature range and meets the heating load requirements of a building. Effectively provide space convection heating air at room temperature to provide comfortable indoor air transportation temperature, so as not to cause a cold airflow effect, and to use environmentally acceptable and safe refrigerants. Other purposes include adding the capacity and efficiency of a heat pump system with a given compressor. According to the first argument of the present invention, a heat pump system adopts a garment containing Chinese National Standard (CNS) Λ4 Regulations (210X297) # that is more than the size of the mixed paper.-(Please read the precautions on the back before filling this page )-Set the central standard of the Ministry of Economic Affairs and the employees' nights together. 'Consumer's Consumption of Shell Workers of the Central Standards Bureau of the Ministry of Land and Economics " Noon A7 __________B7' V. Description of the Invention (2) — _ Other components of the thing have higher Multi-component non-irritating (zeotropic) mixed refrigerants having one or more boiling points, utilizing a number of refrigerants sufficient to meet the system capacity and having a substantial portion of low-pressure components separated by the mixture, and a distillation column and separation The tank is fed with a storage tank for removing low-pressure components from the system mixture. According to another aspect of the present invention, the fluid in the storage tank can be heated to further increase the separation of the low-pressure component from the mixture. According to the argument of the present invention, when the system is operating in the heating mode, the effluent of the condenser can be used to heat the storage tank fluid, thereby supercooling the returned refrigerant. When the low-pressure component has been substantially removed from the system mixture and stored in the storage tank, it may be isolated and does not need to continue the rectification process or any special heating or cooling of the refrigerant v or the entire operation in the heating mode This rectification process can continue during the period. The arguments of the present invention work perfectly with very large amounts of HFC mixtures and other environmentally acceptable refrigerants. -This type of refrigerant that provides R407C works particularly well due to its content of R32, R125 & R134a. The current composition includes R32 (23%), Rl25 (25%) and R134a (low-pressure component) at 52%. However, various combinations of this refrigerant and other HFC's will also operate efficiently. According to another internal compression argument of the present invention, the vapor of the refrigerant is separated by the refrigerant flowing in the system at an equilibrium temperature at a selected pressure, and the equilibrium temperature is between the condenser effluent temperature and the evaporator effluent temperature. After that, the steam enters the compressor substantially at the selected pressure point during its compression stroke. In accordance with the teachings of the present invention, steam separation is accomplished using a watering tank or by providing heat exchange between the liquid and vapor components flowing through the refrigerant. The argument of the present invention provides an increase to the heat pump system of any given compressor -5- Contribution Applicable to China:-I I I I I --- (Please read the precautions on the back before filling this page)
、1T 經濟部中央標準局負工消費合作社印" A7 ___________B7 五、發明説明（3 ) ~~~ ~--- 之效率及容量。 根據本發明’調整該冷凍劑混合物以延伸其有效範園及 有效率地加熱及提供改善之房間入口空氣輸送溫度，以及 可-起利用在選定之中間壓力下分離蒸汽及在一類似受壓 點下於該壓縮機之衝程中施加蒸汽至—入口，以便大幅改 善一熱泵系統之有效實際用途的容量、效率、及有效溫度 範圍。 又 如所附圖面中所示，本發明之其他目的 '特色及優點將 由以下示範實施例之詳細敘述變得更明顯。 第1圖係按照本發明第一論點之雙向熱泵系統示意圖， 指出在選擇該操作模式及實施例之前該系統中所有閥門、 連接管線及各零組件。 第2圖係第1圖系統之一示意圖，只指出以過量冷凍劑充 填該系統期間所使用之有效操作部份。 第3圖係第1圖系統之一示意圖，只指出遵循根據第2圖 於一穩態加熱模式中操作所使用之有效操作零組件。 第4圖係第1圖系統之一示意圖，只指出在精餾期間由中 等容量轉換至該系統之最大加熱能力所使用之有效操作部 份0 第5圖係第1圖系統之一示意圖，只指出在被動式反精餾 (passive derectification)期間建立一冷卻操作所使用之有效 操作零組件。 第6圖係第1圖系統之一示意圖，只指出在加壓反精餾期 間建立一冷卻操作所使用之有效操作零组件。 -6 - 本紙張尺度適用中國國家樣準（CNS ) Λ4規档（210X297公# ) (請先閱讀背面之注意事項再填寫本頁) -='一° A7 B7 經濟郎中pi 五、發明説明（4 第7圖係第1圖系統之—示意圖，只指出在正常之冷卻操 作期間所使用之有效操作零組件。 第8圖係在代表施予熱能時之猶環周期之供電精餾部份 期間可經歷冷凍劑成份之一（質量）圖表，按照本發明之第 一論點説明該系統中所剩下冷凍劑混合物之成份係由在天 然精餾I後义一高Rl34a質量濃度（接近百分之4〇)改變至在 供電精餾之後之少於百分之1〇。 第9圖係孩系統猶環之一熱力圖，説明本發明第二論點 之原理（稱爲級内壓縮）。 第10圖係按照本發明第二論點之—雙向祕系統示意圖。 第11圖係一具有按照本發明之蒸汽入口之渦捲式壓縮機 局部剖面圖。 第12圖係-併人本發明第_及第二論點之雙向熱系系統 之示意圖。 第13圖係按照本發明第二論點之第二實施例之雙向熱泵 系統示意圖。 第14圖係—説明本發明第二論點之第二實施例原理之相 位圖。 現在參考第1圖，按照本發明之—熱泵系統12包含一室 内部伤13及—户外郅份14。該室内部分包含—習知之主盤 管16、％脹閥17、及諸如止回閥18之—單向流動裝置。 除了當該室内部分中之流動係逆時鐘方向時以外，該止回 閥18使得該膨脹闕17不作動。 该户外-P知14包含-習知之主盤管21、腺閥22、及 本紙張尺度適用中國國家兵(cns I - I I I I - II^- - H - 1 _ 訂 (請先閲讀背面之注意事項再填寫本頁) A7 A7 經濟郎失票®黔轉U每f卜.Ul. h CL 21, 1T printed by the Central Standards Bureau of the Ministry of Economic Affairs and Consumer Cooperatives " A7 ___________B7 V. Description of the invention (3) ~~~ ~ --- Efficiency and capacity. According to the present invention, 'the refrigerant mixture is adjusted to extend its effective range and efficiently heat and provide improved room inlet air delivery temperature, and can be used to separate steam at a selected intermediate pressure and at a similar pressure point The steam is applied to the inlet during the stroke of the compressor in order to greatly improve the effective practical use capacity, efficiency, and effective temperature range of a heat pump system. Also as shown in the attached drawings, other objects, features and advantages of the present invention will become more apparent from the detailed description of the following exemplary embodiments. Figure 1 is a schematic diagram of a two-way heat pump system according to the first argument of the present invention, indicating that all valves, connecting lines and components in the system are selected before the operation mode and embodiment are selected. Figure 2 is a schematic diagram of the system of Figure 1 and only indicates the effective operating parts used during filling the system with excess refrigerant. Fig. 3 is a schematic diagram of the system of Fig. 1 and only indicates the effective operating components used in accordance with Fig. 2 for operating in a steady state heating mode. Figure 4 is a schematic diagram of the system of Figure 1 and only indicates the effective operating part used for the conversion from medium capacity to the maximum heating capacity of the system during rectification. Figure 5 is a schematic diagram of the system of Figure 1 and only Indicate the effective operating components used to establish a cooling operation during passive derectification. Figure 6 is a schematic diagram of the system of Figure 1 and only indicates the effective operating components used to establish a cooling operation during pressurized reverse rectification. -6-This paper size applies to Chinese National Standard (CNS) Λ4 specification (210X297 公 #) (Please read the precautions on the back before filling this page)-= '一 ° A7 B7 Economy Lang pi V. Description of the invention ( 4 Figure 7 is a schematic diagram of the system in Figure 1 and only indicates the effective operating components used during normal cooling operation. Figure 8 is during the power rectification part representing the still-cycle cycle when heat is applied It can go through one (mass) chart of the refrigerant composition. According to the first argument of the present invention, the composition of the remaining refrigerant mixture in the system is determined by the high concentration of Rl34a (close to percent) after natural distillation. 4〇) Change to less than 10% after power supply rectification. Figure 9 is a heat map of the loop of the system, illustrating the principle of the second argument of the present invention (called intra-stage compression). The diagram is a schematic diagram of a two-way secret system according to the second point of the present invention. Fig. 11 is a partial sectional view of a scroll compressor having a steam inlet according to the present invention. Schematic diagram of the two-point thermal system. Figure 13 is a schematic diagram of a two-way heat pump system according to a second embodiment of the second argument of the present invention. Figure 14 is a phase diagram illustrating the principle of the second embodiment of the second argument of the present invention. Referring now to Figure 1, according to this The invention—the heat pump system 12 includes an internal injury 13 and an outdoor component 14. The indoor portion includes—a conventional main coil 16, an expansion valve 17, and a one-way flow device such as a check valve 18. Except when the flow in the indoor part is counterclockwise, the check valve 18 keeps the expansion cymbal 17 inactive. The outdoor-P know 14 contains the known main coil 21, gland valve 22, and the paper size Applicable to Chinese National Soldiers (cns I-IIII-II ^--H-1 _ Order (please read the precautions on the back before filling this page) A7 A7 Jirolang Voucher ® Qian Zhuan U every f. Ul. H CL 2
五、發明説明（ 諸如止回閥23之-單邊流動裝置。該户外部份亦包含一用 導管27連接至四通闕28之壓縮機26 ’第i圖中所示閥_ 在-中間位置。該闕門28可藉著諸如_電磁閥”電力或電 子定位’歧當該熱系系統在一冷卻模式時經由導管則 接該導管27至該盤管21，或於加熱操作模式期間(於其他位 置中）經由導管30連接該導管27至該盤管1ό。下文將關於第 2-7圖更充分地敛述這些模式。爲本發明第—論點之目的 ，該壓縮機26可爲任何習知之活塞式或渴捲式或其他型式 壓縮機。冑了併人本發明之級内壓縮論點，如關於下文第 8-10圖所述，一修改渦捲式壓縮機爲較佳；然而假如需要 可使用其他諸如一螺旋、旋轉或往復式壓縮機之壓縮型式 ，以提供該級内壓縮技術。 由一習知吸入儲存器34藉由導管33進给至該壓縮機％， 依該四通闕28之位置而定可由盤管16或盤管21經由導管^ ，36輸入該儲存器34。該儲存器34將有一習知之排油孔（未 示出），用以缓慢地計量該儲存器中所有回流至該壓縮機之 液體，以便補償壓縮機油。 至今所述之設備係習知者。關於第i圖總結根據本發明 之低壓冷凍劑之儲存細節，及關於第2_7圖更充分地説明 足。按照本發明，一低壓冷凍劑儲存槽39包含一藉著導管 41，42連接至閥門B相對兩側之加熱盤管4〇，該閥門B可經 由諸如電磁閥44之任何合適電力或電子機制選擇性地操作 。當該閥門B打開時，該導管41，42及該加熱盤管4〇本質上 不在該系統中。該儲存槽39係由習知之精餾塔47給料，該 本紙張尺度適用中關家 A 7 ' ____B7 五、發明説明（6 ) (請先閱讀背面之注意事項再填寫本頁) 精餾塔以一方式會同習知之液體/蒸汽分離器48運作，使 得當關上一對閥門A時，該儲存槽39、精餾塔47及分離器 48本質上係在該系統之外。當打開該二閥門時，經由諸如 電磁閥49之任何合適電力或電子機制，該導管36中高度蒸 發之返回冷凍劑係經由右閥門A 50給入該分離器48。該液 體傾向於往下流經該精館塔47。一非刺激性（zeotropic)冷滚 劑混合物之較不易揮發（低壓）冷凍劑之蒸汽傾向於以一習 知方式冷凝在該精餾塔47内之填料上。該混合物之較易揮 發（高壓）成份之蒸汽將傾向由該液體分開及將經由該左側 閥門A 51通過導管52進入該導管35，俾能返回該吸入儲存 器34。按照本發明，使該閥門A打開，該系統係填入充分 之冷凍劑，以致當分離該低壓成份時該系統容量可充滿該 高壓成份，而R407C將爲該系統所額定之最高周遭溫度下 所需充填之兩倍（或更多）。當打開該閥門A及關閉該閥門B 時，該返回冷凍劑將流經該導管41及42經過該加熱盤管40 ，而傾向於加熱該儲存槽39中之液體，造成該較易揮發成 份蒸發及向上流經該精餾塔47。某些較不易揮發成份之向 上流動蒸汽於其向上流動期間因冷卻而將冷凝，及返回至 該儲存槽39。來自該盤管40之熱量傾向於增加該精餾塔47 中低壓冷凍劑與高壓冷凍劑之分離。取代該分離器48，可 利用一流量分配器；但一簡單之分離器架構係很有成本效 率及合適的。 根據本發明，可經由諸如電磁閥55之任何合適電力或電 子機制選擇性地打開或關閉閥門C達成反精餾，以經由導 -9- 本紙張尺度適用中國國家摞準（CNS ) A4規格（210X297公^ ) ~ A 7 f ___B7五、發明説明（7 ) 管56，57連接該儲存槽39之底部至該眞空儲存器34。於一 實施例中，該儲存槽39可垂直地安裝至高於該儲存器34之 入口，以致液體能經由重力由該儲存槽39流至該儲存器34 。於另一實施例中，當想要反精餾時可關閉該閥門A、B及 C，加熱該儲存槽39、精餾塔47及分離器48中之流體直至 有一充分之壓力積聚，以致閥門C之打開將迫使該液體經 由該導管56，57流出該儲存槽39及進入該眞空儲存器34。 於精餾或反精餾期間，假如想要時可使用一浸入式電熱器 代替該盤管40、該導管41及42及該閥門B。然而，所示包 含該盤管40之設備係更經濟，因爲其將避免使用電能及將 使返回之冷;東劑過冷。 雖然特別之冷凍劑成份非本發明所關心者，一示範之商 業上現成可用冷凍劑爲R407C，其中R32之質量百分比爲百 分之23、R125爲百分之25、及R134a爲百分之52。依理想之 加熱及冷卻所想要之變化範園可利用一些其他HFC冷凍劑 之非刺激性（zeotropic)混合物。 按照本發明，當利用第1圖之熱泵系統加熱該室内部份 13時，藉著有效地移去該冷凍劑混合物中一大部份之最低 壓（最不易揮發）成份而變更該冷凍劑成份至一較易揮發混 合物即可改善其效率，可擷取熱量之户外溫度能顯著較低 ，及眞正進入房間之室内溫度可大幅升高，以便避免一寒 冷氣流效果。如所已知，R407C關於其R134a成份及其他成 份係非刺激性（zeotropic)。如此，該R134a成份能以一已知 方式經由選擇性之蒸發及冷凝由該R32及R125成份分離。 -10- 本纸張尺度適用中國國家標隼（CNS )八4規格（210><297公处1 " (請先閲讀背面之注意事項再填寫本頁) A7 ， 厂· I _ ------—__jp 五、發明説明（8 ) ~ — 本發明以一改善方式完成這目的，而不需該冷凍劑之穩態 加熱或冷卻以於加熱操作期間維持該精餾處理，及比至今 所可達到（方式遠較有效率地達成各成份產量。然而，本 發明可過及孩加熱期間持續與精館一起使用，因爲使用返 回i冷凍劑以加熱孩儲存槽中之流體而使該冷凍劑過冷及 增加效率。_ c all 本發明心一論點係以冷凍劑過量充填該系統達其容量之 兩倍或甚至更多。爲達成此目的，過量之冷凍劑係儲存於 I儲存槽39中。於第2圖中，該架構係顯示爲該系統可能 A最初充填，而在一加熱模式中操作。定位該四通閥28以 引導該壓縮機26之流出物經過該導，管3〇及用作一凝結器之 盤管16,及承接來自現在用作蒸發器之盤管21之流動，及 引導其至該導管36用以返回該儲存器34，藉此加熱該室内 部分。此外打開該閥門A，造成該分離器48連接至該導管 36及52，以致當該系統最初開始時可有一高液體含量之冷 凍劑由孩蒸發器21返回，而將特別提供一大部份液體至該 分離器48以及至該儲存器34。此外，打開該閥門B以致該 加熱器盤管40本質上係於該系統之外。關上該閥門c，因 此該儲存槽39之底部及該儲存器34之間無聯接。於該架構 中，液體及蒸汽二者傾向於在該精餾塔47内流動，該液體 以一習知方式向下流至該儲存槽39及蒸汽傾向於向上流至 該分離器48。該混合物之較易揮發成份將傾向於保留或進 入蒸汽相，反之該混合物（R134a)之較不易揮發成份將傾向 於保留或進入該液相及藉此往下流至該儲存槽39。在某些 -11 - 本紙張尺度適用中國國本標率（CNS〉A4規柏（2】〇'X 29*?公舞） —_ ~ -—一 經濟部中央標準局員工消費合作社印製 A 7 , __B7 1五、發明説明（9 ) 時期之後，當該系統已達至平.衡時，該系統（儲存槽39外侧） 中R134a之質量百分比由該混合物百分之52減少至約百分之 40，及該儲存槽39將包含某些數量之R32及R125。在此及 時關上該閥門A，謗捕該儲存槽39中之液體，如第3圖所示 。在打開該閥門A時期該系統將不會繼續操作，因爲這將 造成所有壓縮機油聚積於該儲存槽39中。當適中之加熱需 求可滿足高於約攝氏40度之外側空氣溫度時，第3圖百分 之40之R134a混合物可能對北半球之春天及秋天有用。注意 不須加熱或冷卻以維持百分之40之混合物。 當外侧空氣溫度可依關於第4圖所述方式降至完全低於 攝氏40度時，本發明容納更猛烈之加熱需求。於第4圖中 ，該架構正好與第2圖之架構相同，除了關閉該閥門B之事 實外，而造成返回之冷凍劑由該導管19經過該浸入式加熱 器40及該導管41直接流入該導管42，及由該處至該膨脹閥 22。這造成該儲存槽39中之液體以及該儲存槽及精餾塔47 中之液體及蒸汽之溫度增加，藉此以關於其個別揮發性之 程度造成混合物各成份蒸發。部份R407C將蒸發及流入該 精餾塔47 ;當其上昇時，該蒸汽將變得更冷，及一些蒸汽 將冷凝在該填料上，導致R407C之往下流動退入該儲存槽 39。該較易揮發成份（R32及R125)將傾向於停留在蒸汽相中 ，藉此抵達該分離器48以通過該導管52進入該儲存器34。 以此方式可達至一新的平衡，其中依所有系統參數而定 R134a之百分比可爲非常低。如第8圖所示已輕易地達成一 少於百分之5之R134A成份。吾人相信可經由利用習知之調 -12 - 本紙張尺度適用中國國家標準（CNS ) A4規桔（210X297公 I II- ! I - - I- -I - /农 - - - - I (請先閱讀背面之注意事項再填寫本頁) 經濟部中央標隼苟員-1-肖犛釜乍土 _0_泛 A7 --—_________B7 五、發明説明（1〇 ) ――" -- 整万法論調整系統參數而輕易地達成部份百分比。 當依熱量、充填量及其他參數而定已達至典型花費約半 小時至兩小時左右之平衡時，即不需繼續該精顧製程。所 、可如第3圖所示關上該閥門A及打開該閥門b。於第3 圖中該木構係與第4圖之架構相同，除了關上該閥門A及 再一次打開閥門B外，藉此由該系統有效地移去該儲存槽 其加熱器40、及導管41及42，以及該精餾塔47及分離 器48。現在該系統中之混合物有約百分之5或更少之幻3切 ，因爲大部份R134a係儲存於該儲存槽39中。注意不須加熱 或冷卻以維持該混合物。 在穩態加熱期間，對於第3圖所示架構，霜可能堆積在 妓蒸發器21上。於此一情況中，反轉該四通閥28以便造成 該架構與第7圖之架構相同，藉此定期地施行約幾分鐘之 除霜運轉。所述除霜係習知者。不論何時該系統具有過多 容量時’其運轉將無效率。當加熱需求已消退（諸如北半球 之春天）及需要冷卻時，該系統中運轉之冷凍混合物必得恢 復至包含百分之40之R134a混合物。藉著第5圖及/或第6圖 所示之反精餾達成此目的。現在參考第5圖，該設備係描 述爲使得該閥門A及C關上及該閥門B打開，使該四通閥28 連接該壓縮機26至該盤管21以致第6圖中之流動爲逆時鐘 方向；該盤管21正用作一凝結器及該盤管16正用作一蒸發 器以冷卻該室内部分。現在打開該閥門C，藉此經由導管 56 ’ 57連接該儲存槽39底部至該儲存器34。於最簡單之實 施例中’該儲存槽39實際上係垂直地放在該儲存器34上方 -13· 本紙張尺度適用中國國家標準（CNS ) Λ4規掊（210X297公梦） IK 11 -1 ^^^1 1 1 nn Hi ^H^J. n^· n I^m m (諳先閱讀背面之注意事項再填寫本頁) 訂 .I - - -I II 8 -1 A7 ____ —_B7 五、發明説明（11) ’及因此該儲存槽39中之液體將完全流入該儲存器34。假 如於本發明之任何實施例中該儲存器34不能充分定位在該 儲存槽39下方以確保適當之流動，如第6圖所示可達成加 壓反精餾。於第6圖中，使閥門B關上，來自該盤管21之凝 結器流出物係引導經過該儲存槽39之加熱器40而保持關閉 該閥門A及C。這將造成該儲存槽39中之壓力堆積。在已充 分加強該壓力後，然後經由再—次打開該閥門B及打開該 閥門C而保持關閉該閥門A即可將該設備轉換至第5圖所杀 者，該儲存槽39中之壓力迫使液體流出該儲存槽39經過該 導管56 ’ 57及進入該儲存器34。當然假如想要時對於某些 重力式流動，加壓該儲存槽39可與關於該儲存器34具有一 合適高度之儲存槽39會同使用。 當完成反精餾時，可如第3圖所示或如第7圖所示分別實 行加熱或冷卻，而如第8圖所示具有百分之4〇之Rl34a混合 物。第7圖係與第3圖相同，除了該四通閥28係定位供冷卻 外。該加熱器40及導管41，42、該儲存槽39 '精餾塔47及 分離器48、及該導管56與57本質上在該系統中。 現在參考第10圖，本發明之第二級内壓縮論點利用一灌 水槽60以由局部膨脹之凝結器流出物分離蒸汽，及將一導 管61上方之蒸汽施加至一修改壓縮機26&之輔助入口 Q，該 入口係在該壓縮衝程之一選定中間受壓點。於第1〇圖中， 定位該四通閥28以造成該熱泵系統在冷卻模式中操作。該 盤管2i正用作凝結器及其流出物流經第二個四通閥“，經 由諸如電磁閥31a之任何合適電力或電子機制與該四通閥28 -14· 本紙张尺度適月)八^^7 2丨〇 X 297^*5----- 广讀先閲讀背而之注意事項真填寫本買) 取· 、1Τ A7 ---—_________Β7___ 五、發明説明（12) 一 同步地控制該第二個四通閥65。該流動沿著一導管66通過 膨脹閥67及至該灌水槽6〇之入口 68。液體由該蒸汽分開及 通過第匕膨脹閥69及—導管至該四通閥Μ，此後其於一導 管71中載送至包含該室内部份13中盤管16之蒸發器。然後 該冷凍劑沿著該導管30通過該四通閥28、該導管36及進入 該儲存器34a，即本實施例中所習知者。 該製程係説明在第9圖中，其中離開該壓縮機26a及進入 該導管27之冷凍劑係在最高壓力及焓，如在第9圖中之點τ 。當該冷凍劑流經該凝結器時，其損失熱量及因此損失焓 ’以致其由該凝結器以在高壓之低给顯現，如點U所示。 當該冷凍劑通過第一膨脹閥67時，該壓力於平衡時降至一 選定之中間壓力，並在該凝結器溫度及該蒸發器溫度間之 一溫度，造成該液體如點V所示變成雙相。在每一情況中 該選定之中間壓力係決定爲最佳者，因一系統設計係在最 大效率及最大容量之間妥協，如每一情況中所需者藉著依 模型製作或憑輕驗觀察得來。於一些情況中，實質上可能 爲一沿著該壓縮機壓縮衝程中途之壓力。該蒸汽沿著該導 管61通過及在等於該選定中間壓力之壓縮機衝程中之一受 壓點進入該恩縮機26a入口 62，如點W所示。這導致一較高 之系統容量。該冷凍劑之剩餘部份離開該灌水槽，如點X 所示之液體，及當該冷凍劑通過該膨腺閥69在點γ抵達最 低壓時其又變成雙相。然後該雙相冷凍劑在其衝程之最低 壓點通過該蒸發器及該儲存器34a、進入該壓縮機，如點Z 所示。 -15- Ϊ、紙張纽關㈣醉料(CNS ) Λ4規格（210Χ297公楚) '" (諳先閱讀背面之注意事項再填寫本頁) 裝. -a A7 ™~·"~~~_________B7 五、發明説明（13) ~~" 孩壓縮機26a可爲一活塞式壓縮機或任何修改成大約沿著 其壓縮衝程中途具有—入口之其他合適壓縮機。然而，如 第11圖所π實行本發明之一較佳模式係利用一渦捲式壓縮 機75，其以經過具有一入口 77之外殼76及經過一軌道式渦 捲片78之剖面所顯示。該外殼76之内部形成具有一壓力室 底部S1及一壓力室頂部（未示出）之壓力室。當該軌道式渦 捲片78繞著固定式渦捲片82運轉及在其内時，冷凍劑蒸汽 係在二點83 ’ 84夾帶於該二渦捲片之間，該二點83，84包 含二壓縮衝程之入口，每一點發生在該固定式渦捲片82之 每一側。該壓縮機可具有二移動式渦捲片。按照本發明， 每一壓縮路控大約在沿著該壓縮衝程之選定屢力點具有一 對應之級内壓縮蒸汽入口。於第U圖中，該入口包含四個 方便經由鐵孔形成之孔口 85 ’ 86。然而，該入口可爲其他 形狀，只要其具有適當尺寸及定位有最大之性能。於第u 圖中，該入口係鄰接該固定式渦捲片82之個別邊緣，但其 可位於任何橫側位置中。 本發明在一較鬲之中間受壓點經由取用進入該壓縮機之 一大部份冷凍劑質量流導致冷凍劑質量流之增加，藉此增 加一已知蒸發器及凝結器尺寸及該系統中已知冷凍劑數量 之冷卻（或加熱）效果。需要一更強大之驅動馬達。然而， 即使具有一增加之電力輸入需求，已改善聲體效率及;eer。 可使用如第9 -11圖所示利用一灌水槽之級内壓縮以用於 第10圖所不架構中之冷卻（或藉著反轉閥門28，65而用於加 熱）’而無如前文關於第1-8圖所述來自調整該冷凍劑成份 -16- 孓紙張尺廋诮州中國國家標埤ΓτΝ^7Λϋ ( 210X297公釐） --------- (諳先閲讀背面之注意事項再填寫本頁) 袈. 訂 .! 1 m HI ? · A7 ______________B7_ 五、發明説明（14) - 之任何增強作用。在另一方面，本發明之二論點最好在實 行加熱以及冷卻之任何狀況中一起利用。第12圖説明—併 入本發明在此二論點之系統。於第12圖之系統中，所有零 組件以與前文所述完全相同之方式操作，無任一特色彼此 牴觸。 本發明之級内壓縮論點亦可利用一熱交換器代替—灌水 槽而實現。於第13圖中，該凝結器流出物係如前用該四通 閥65引導至膨脹閥67。然而，該流動分濶及部份流動通過 一導管至一熱交換器91之放熱（熱釋出）部份92，該熱交換 器91之吸熱（熱提供）93部份由該膨脹閥67承接膨脹之凝結 器流出物。參考第14圖之相位圖，該導管27及29中之壓縮 機26a^出物在點T具有高於在該系統中任何其他點之壓力 及焓。當該冷凍劑通過該凝結器時，其放熱及因此損失給 ，而以點U所示之壓力及焓離開該凝結器。部份流動通過 該膨賬閥67及遭受減壓而抵達點ν'。該導管90中之液體通 過該熱交換器而放出熱量至由該閥門67進入該熱交換器之 蒸汽。這增加該蒸汽之焓以致其達至第14圖中之點w，其 狀況爲該蒸Η沿著該導管61通過並在入口 62進入該壓縮機 26a。經由放熱’該熱交換器部份91中之液體損失更多焓地 抵達點X'。然後該液體通過膨脹閥69，在點γι膨脹變成雙 相。·然後該冷凍劑通過該蒸發器，吸熱尽蒸發以抵.達點Ζ 。然後該蒸汽在其規定入口經由該導管30, 36及33進入該 壓縮機》 第13圖之熱交換器實施例可經由切換該閥門28, 65用於 -17- 本紙張尺度谜用中國國家播苹（) Λ4規格（210X297公着） (請先閲讀背面之注意事項再填寫本頁) 袈· -訂 五、發明説明（l5) A7 B7 加熱及能以第10及12圖明顯可見之方彳 式與本發明之其他論 點結合。 吾人巴用114〇7〇當作冷康劑操作之觀點敘述本發明。然 而，本發明之第一論點同樣應用於具有二或更多成份之非 刺激性（zeotropic)冷凍劑。吾人已用室内及户外部分之觀點 敘述本發明，但主要盤管當然可具有其他類似之關係。已 敘述本發明利用膨脹閥，但在本發明範園内無論何時只要 適當時可利用諸如毛細管等其他膨脹裝置。本發明可與一 變速壓縮機一起使用以在加熱及冷卻操作之間改善容量及/ 或效率。第10 ’ 12及13圖之實施例能以一習知方式如所示 在該四通閥前面使用多個膨脹裝置及旁通闕，以便正好在 進入一盤管之前造成冷凍劑膨脹。所有前面所述係與本發 明不對題。 18- 本紙張尺度通用中國國家標準（CNS ) Λ4規格（2丨〇χ297公釐） (#先閱讀背面之注意事項再填寫本頁) 袈. 、1ΤV. Description of the invention (such as non-return valve 23-unilateral flow device. The outdoor part also includes a compressor 26 connected to the tee 28 through a duct 27 'The valve shown in the i-th position is in the middle position The door 28 can be connected to the coil tube 21 through the conduit when the thermal system is in a cooling mode by means of electric or electronic positioning such as a _solenoid valve, or during the heating operation mode (in the In other positions) the conduit 27 is connected to the coil 1 through the conduit 30. These modes will be described more fully with reference to Figures 2-7. For the purpose of the first argument of the present invention, the compressor 26 may be any custom Known piston or thirsty scroll compressors or other types of compressors. Combining with the internal compression argument of the present invention, as described in Figures 8-10 below, it is better to modify scroll compressors; however, if necessary, Other compression types, such as a screw, rotary, or reciprocating compressor, can be used to provide this stage of compression technology. A conventional suction reservoir 34 is fed to the compressor by a conduit 33, according to the four-way 阙The position of 28 can be passed by coil 16 or coil 21 Conduit ^, 36 enters the reservoir 34. The reservoir 34 will have a conventional oil drain hole (not shown) to slowly meter all the liquid in the reservoir back to the compressor in order to compensate the compressor oil The device described so far is known to the person. About figure i summarizes the details of the storage of the low-pressure refrigerant according to the present invention, and more fully shows about figures 2-7. According to the present invention, a low-pressure refrigerant storage tank 39 contains Once connected to heating coils 40 on opposite sides of valve B via conduits 41, 42, the valve B can be selectively operated via any suitable electrical or electronic mechanism such as a solenoid valve 44. When the valve B is opened, the valve B The pipes 41, 42 and the heating coil 40 are not in the system in essence. The storage tank 39 is fed by the conventional distillation column 47, and this paper is applicable to Zhongguanjia A 7 '____B7 V. Description of the invention (6 ) (Please read the notes on the back before filling this page) The rectification column operates in a manner that is familiar with the conventional liquid / steam separator 48, so that when a pair of valves A is closed, the storage tank 39, the rectification column 47 and The separator 48 is essentially tied to Outside the system. When the two valves are opened, the highly evaporated return refrigerant in the conduit 36 is fed into the separator 48 via the right valve A 50 via any suitable electrical or electronic mechanism such as a solenoid valve 49. The liquid Tends to flow down through the refinery tower 47. The vapor of a less volatile (low pressure) refrigerant from a non-irritating cold roll mixture tends to condense the packing in the rectification tower 47 in a conventional manner. The vapors of the more volatile (high-pressure) components of the mixture will tend to be separated by the liquid and will enter the conduit 35 through the conduit 52 through the left valve A 51 and return to the suction reservoir 34. According to the present invention, the The valve A is opened, and the system is filled with sufficient refrigerant, so that when the low-pressure component is separated, the system capacity can be filled with the high-pressure component, and R407C will be twice the filling required at the maximum ambient temperature rated by the system (Or more). When the valve A is opened and the valve B is closed, the return refrigerant will flow through the pipes 41 and 42 through the heating coil 40, and tends to heat the liquid in the storage tank 39, causing the more volatile component to evaporate And upwards through the rectification column 47. The upwardly flowing steam of some of the less volatile components will condense due to cooling during its upward flow, and return to the storage tank 39. The heat from the coil 40 tends to increase the separation of low-pressure refrigerant from high-pressure refrigerant in the rectification column 47. Instead of the separator 48, a flow distributor may be used; but a simple separator architecture is very cost-effective and suitable. According to the present invention, anti-rectification can be achieved by selectively opening or closing valve C via any suitable electrical or electronic mechanism, such as solenoid valve 55, in order to apply the Chinese National Standard (CNS) A4 specification (-) 210X297 male ^) ~ A 7 f ___B7 V. Description of the invention (7) Pipes 56, 57 connect the bottom of the storage tank 39 to the empty storage 34. In one embodiment, the storage tank 39 may be mounted vertically above the inlet of the storage 34 so that liquid can flow from the storage tank 39 to the storage 34 by gravity. In another embodiment, when reverse rectification is desired, the valves A, B, and C may be closed, and the fluid in the storage tank 39, the rectification column 47, and the separator 48 may be heated until a sufficient pressure is accumulated, so that the valve The opening of C will force the liquid out of the storage tank 39 and into the empty reservoir 34 via the conduits 56, 57. During rectification or reverse rectification, if desired, an immersion heater can be used in place of the coil 40, the pipes 41 and 42, and the valve B. However, the equipment shown including the coil 40 is more economical because it will avoid the use of electrical energy and will cool the return; the agent is too cold. Although the particular refrigerant composition is not of interest to the present invention, a demonstration commercially available refrigerant is R407C, of which R32 is 23% by mass, R125 is 25%, and R134a is 52% . The desired change in heating and cooling can be achieved using a non-irritating (zeotropic) mixture of other HFC refrigerants. According to the present invention, when the indoor portion 13 is heated by the heat pump system of FIG. 1, the refrigerant composition is changed by effectively removing a large part of the minimum pressure (least volatile) component of the refrigerant mixture. To a more volatile mixture can improve its efficiency, the outdoor temperature that can capture heat can be significantly lower, and the indoor temperature of the room entering the room can be greatly increased, in order to avoid a cold airflow effect. As is known, R407C is zeotropic with regard to its R134a and other components. In this way, the R134a component can be separated from the R32 and R125 components in a known manner by selective evaporation and condensation. -10- This paper size is applicable to China National Standard (CNS) 8-4 specifications (210 > < 297 公 部 1 " (Please read the precautions on the back before filling this page) A7, factory · I _- ----—__ jp V. Description of the invention (8) ~ — The present invention accomplishes this in an improved manner without the need for steady-state heating or cooling of the refrigerant to maintain the rectification process during the heating operation, and the ratio What has been achieved so far (in a much more efficient way to achieve the yield of each component. However, the present invention can continue to be used with the fine hall during the heating period, because the use of return refrigerant to heat the fluid in the storage tank of the child makes it Refrigerant subcooling and increased efficiency._ c all The main idea of the present invention is to overfill the system with refrigerant in excess of twice or even more of its capacity. To achieve this, excess refrigerant is stored in the I storage tank 39. In Figure 2, the architecture is shown as the system may be initially filled and operated in a heating mode. The four-way valve 28 is positioned to direct the effluent from the compressor 26 through the guide, tube 3 〇 and coil 16 used as a condenser, and to undertake Flow from the coil 21 now used as an evaporator, and directing it to the conduit 36 for return to the reservoir 34, thereby heating the indoor part. In addition, opening the valve A causes the separator 48 to be connected to the conduit 36 and 52, so that when the system is initially started, a high liquid content refrigerant can be returned from the child evaporator 21, and a large part of the liquid will be provided in particular to the separator 48 and to the reservoir 34. In addition, open The valve B so that the heater coil 40 is essentially outside the system. The valve c is closed, so there is no connection between the bottom of the storage tank 39 and the reservoir 34. In this architecture, liquid and steam two They tend to flow in the rectification column 47, the liquid flows down to the storage tank 39 in a conventional manner and steam tends to flow up to the separator 48. The more volatile components of the mixture will tend to remain or Into the vapor phase, on the other hand, the less volatile components of the mixture (R134a) will tend to retain or enter the liquid phase and thereby flow down to the storage tank 39. In some -11-this paper size applies China's national standard rate (CNS> A4 Bai (2) 〇'X 29 *? Public dance) —_ ~ -— Printed by A7, __B7, a consumer cooperative of the Central Standards Bureau of the Ministry of Economic Affairs. 5. After the period of the invention (9), when the system has reached At equilibrium, the mass percentage of R134a in the system (outside of storage tank 39) is reduced from 52% of the mixture to about 40%, and the storage tank 39 will contain some amounts of R32 and R125. Here Close the valve A in time to catch the liquid in the storage tank 39, as shown in Figure 3. During the opening of the valve A, the system will not continue to operate because it will cause all the compressor oil to accumulate in the storage tank. 39 in. When moderate heating requirements are sufficient to meet outside air temperatures above about 40 degrees Celsius, the R134a mixture at 40 percent in Figure 3 may be useful for spring and autumn in the northern hemisphere. Note No heating or cooling is required to maintain a 40% mixture. When the outside air temperature can be reduced completely below 40 degrees Celsius in the manner described in relation to Figure 4, the present invention accommodates a more intense heating demand. In Figure 4, the structure is exactly the same as that in Figure 2. Except for the fact that the valve B is closed, the returned refrigerant flows directly from the conduit 19 through the immersion heater 40 and the conduit 41 into the A conduit 42 and from there to the expansion valve 22. This causes the temperature of the liquid in the storage tank 39 and the liquid and steam in the storage tank and rectification column 47 to increase, thereby causing the components of the mixture to evaporate to a degree related to their individual volatility. Part of the R407C will evaporate and flow into the rectification column 47; when it rises, the steam will become colder, and some of the steam will condense on the packing, causing the R407C to flow downward into the storage tank 39. The more volatile components (R32 and R125) will tend to stay in the vapor phase, thereby reaching the separator 48 to enter the reservoir 34 through the conduit 52. A new equilibrium can be achieved in this way, where the percentage of R134a can be very low depending on all system parameters. As shown in Figure 8, a R134A content of less than 5 percent has been easily achieved. I believe that through the use of the known tune -12-This paper size applies the Chinese National Standard (CNS) A4 standard orange (210X297 male I II-! I--I- -I-/ Nong-----I (Please read first Note on the back, please fill out this page again.) Central Ministry of Economic Affairs of the People's Republic of China -1- Xiao 牦 Ku Zhatu __Pan A7 ---_________ B7 V. Description of Invention (1〇) —— " Adjust the system parameters to easily reach a percentage. When the balance that takes about half an hour to about two hours has been reached depending on the heat, filling amount and other parameters, it is not necessary to continue the intensive process. So, you can Close the valve A and open the valve b as shown in Figure 3. In Figure 3, the wooden structure is the same as the structure of Figure 4, except that the valve A is closed and the valve B is opened again. The system effectively removes the storage tank with its heater 40, and the pipes 41 and 42, and the rectification column 47 and separator 48. The mixture in the system now has about 5 percent or less magic 3 cuts, Because most of R134a is stored in the storage tank 39. Note that no heating or cooling is necessary to maintain the mixture. During steady-state heating, for the architecture shown in Figure 3, frost may accumulate on the prostitute evaporator 21. In this case, the four-way valve 28 is reversed so that the structure is the same as the structure shown in Figure 7, whereby A defrost operation of about a few minutes is performed regularly. The defrost is known. Whenever the system has too much capacity, its operation will be inefficient. When heating needs have subsided (such as the northern hemisphere spring) and cooling is needed The frozen mixture running in this system must be restored to a R134a mixture containing 40%. This is achieved by reverse rectification as shown in Figure 5 and / or Figure 6. Now referring to Figure 5, the equipment is It is described that the valves A and C are closed and the valve B is opened, so that the four-way valve 28 is connected to the compressor 26 to the coil 21 so that the flow in FIG. 6 is counterclockwise; the coil 21 is being used as A condenser and the coil 16 are being used as an evaporator to cool the indoor part. The valve C is now opened, thereby connecting the bottom of the storage tank 39 to the storage 34 via a conduit 56'57. In the simplest implementation Example 'The storage tank 39 is actually Placed vertically above the storage 34 -13 · This paper size applies Chinese National Standard (CNS) Λ4 Regulation (210X297 public dream) IK 11 -1 ^^^ 1 1 1 nn Hi ^ H ^ J. N ^ · n I ^ mm (谙 Please read the notes on the back before filling in this page). I---I II 8 -1 A7 ____ —_B7 V. Description of the invention (11) 'and therefore the liquid in the storage tank 39 will Completely flows into the reservoir 34. If the reservoir 34 cannot be positioned sufficiently below the storage tank 39 in any embodiment of the present invention to ensure proper flow, pressurized reverse rectification can be achieved as shown in FIG. In Figure 6, the valve B is closed, and the condenser effluent from the coil 21 is guided through the heater 40 of the storage tank 39 to keep the valves A and C closed. This will cause the pressure in the storage tank 39 to build up. After the pressure has been sufficiently strengthened, the device can be switched to the killer in Figure 5 by re-opening the valve B and opening the valve C while keeping the valve A closed. The pressure in the storage tank 39 forces Liquid flows out of the storage tank 39 through the conduit 56'57 and into the storage 34. Of course, if certain gravity flow is desired, the storage tank 39 may be used in combination with a storage tank 39 having a suitable height with respect to the reservoir 34. When reverse rectification is completed, heating or cooling may be performed separately as shown in Figure 3 or as shown in Figure 7, while having a Rl34a mixture of 40% as shown in Figure 8. Fig. 7 is the same as Fig. 3, except that the four-way valve 28 is positioned for cooling. The heater 40 and the ducts 41, 42, the storage tank 39 ', the distillation column 47 and the separator 48, and the ducts 56 and 57 are essentially in the system. Referring now to FIG. 10, the second-stage internal compression argument of the present invention utilizes an irrigation tank 60 to separate steam from a locally expanded condenser effluent, and to apply steam above a duct 61 to a modified compressor 26 & Inlet Q, which is at a selected intermediate compression point on one of the compression strokes. In Figure 10, the four-way valve 28 is positioned to cause the heat pump system to operate in a cooling mode. The coil 2i is being used as a condenser and its effluent flows through a second four-way valve, and via any suitable electrical or electronic mechanism such as a solenoid valve 31a, and the four-way valve 28 -14 ^^ 7 2 丨 〇X 297 ^ * 5 ----- Read extensively, read the back of the note and fill in the purchase)) Take, 1T A7 ---_________ B7___ V. Description of the invention (12) Controls the second four-way valve 65. The flow passes through an expansion valve 67 and an inlet 68 to the irrigation tank 60 along a conduit 66. The liquid is separated by the vapor and passes through the expansion valve 69 and the conduit to the four-way The valve M is thereafter carried in a conduit 71 to an evaporator containing the coil 16 in the indoor portion 13. The refrigerant then passes along the conduit 30 through the four-way valve 28, the conduit 36 and into the reservoir. 34a, which is known in this embodiment. The process is illustrated in FIG. 9, where the refrigerant leaving the compressor 26a and entering the conduit 27 is at the highest pressure and enthalpy, as shown in FIG. Point τ. When the refrigerant flows through the condenser, it loses heat and therefore loses enthalpy 'so that it is caused by the condensation It appears at a low pressure, as shown by point U. When the refrigerant passes through the first expansion valve 67, the pressure drops to a selected intermediate pressure at equilibrium, and at the condenser temperature and the evaporator temperature One of the temperatures causes the liquid to become biphasic as shown by point V. In each case, the selected intermediate pressure is determined to be the best, because a system design compromises between maximum efficiency and maximum capacity, such as What is required in each case is obtained by making a model or by light observation. In some cases, it may be substantially a pressure along the compression stroke of the compressor. The steam passes along the duct 61 and A pressure point at the compressor stroke equal to the selected intermediate pressure enters the inlet 62 of the shrink compressor 26a, as shown at point W. This results in a higher system capacity. The remainder of the refrigerant leaves the irrigation water Trough, the liquid as indicated by point X, and when the refrigerant reaches the minimum pressure at point γ through the expansion valve 69, it becomes biphasic again. The biphasic refrigerant then passes through the evaporation at the lowest pressure point of its stroke. Container and the storage 34a, The compressor, as shown by point Z. -15- Ϊ, paper button off the paper (CNS) Λ4 specifications (210 × 297 public Chu) '" (谙 Please read the precautions on the back before filling this page) Install.- a A7 ™ ~ · " ~~~ _________ B7 V. Description of the Invention (13) ~~ " The compressor 26a may be a piston compressor or any other modified suitable to have approximately along the middle of its compression stroke-other suitable for the inlet Compressor. However, a preferred mode of carrying out the invention as shown in FIG. 11 is to use a scroll compressor 75 which passes through a casing 76 having an inlet 77 and a rail-shaped scroll 78 Displayed. The inside of the casing 76 forms a pressure chamber having a pressure chamber bottom S1 and a pressure chamber top (not shown). When the orbiting scroll 78 is orbiting the fixed scroll 82 and in it, the refrigerant vapor is entrained between the two scrolls at 83 o'clock. The two points 83, 84 include At the entrance of the two compression strokes, each point occurs on each side of the fixed scroll 82. The compressor may have two movable scrolls. According to the present invention, each compression control has a corresponding compressed steam inlet at a selected level of repeated force along the compression stroke. In Figure U, the inlet contains four apertures 85 '86 which are conveniently formed through iron holes. However, the inlet can be of other shapes as long as it is properly sized and positioned for maximum performance. In the u-th figure, the inlet is adjacent to an individual edge of the fixed scroll 82, but it can be located in any lateral position. The present invention increases the refrigerant mass flow by increasing a large part of the refrigerant mass flow into the compressor through taking at a relatively intermediate pressure point, thereby increasing a known evaporator and condenser size and the system. The cooling (or heating) effect of the amount of refrigerant is known. A more powerful drive motor is needed. However, even with an increased power input demand, sound body efficiency and eer have been improved. The use of intra-stage compression of a watering tank as shown in Figures 9-11 can be used for cooling in the structure not shown in Figure 10 (or for heating by reversing the valves 28, 65). About adjusting the composition of the refrigerant as described in Figure 1-8 -16- 孓 Paper ruler 廋 诮 Chinese National Standard 埤 ΓτΝ ^ 7Λϋ (210X297 mm) --------- (谙 Read the first Note for refilling this page) 袈. Order.! 1 m HI? · A7 ______________B7_ 5. Description of the Invention (14)-Any enhancement. On the other hand, the two arguments of the present invention are best used together in any situation where heating and cooling are performed. Figure 12 illustrates a system incorporating both aspects of the present invention. In the system shown in Figure 12, all components operate in exactly the same way as described above, without any features conflicting with each other. The intra-stage compression argument of the present invention can also be realized by using a heat exchanger instead of an irrigation tank. In Fig. 13, the condenser effluent is guided to the expansion valve 67 by the four-way valve 65 as before. However, the flow branch and part flow through a duct to a heat release (heat release) part 92 of a heat exchanger 91, and the heat absorption (heat supply) 93 part of the heat exchanger 91 is taken over by the expansion valve 67 Expansion condenser effluent. Referring to the phase diagram of Fig. 14, the output of the compressor 26a in the ducts 27 and 29 has a higher pressure and enthalpy at point T than at any other point in the system. As the refrigerant passes through the condenser, it exotherms and therefore loses to, leaving the condenser at the pressure and enthalpy indicated by point U. Part of the flow passes through the expansion valve 67 and is subjected to decompression to reach the point ν '. The liquid in the conduit 90 passes through the heat exchanger to release heat to the steam entering the heat exchanger through the valve 67. This increases the enthalpy of the steam so that it reaches the point w in FIG. 14 in the condition that the steam maggot passes along the duct 61 and enters the compressor 26a at the inlet 62. Via exotherm ' the liquid loss in the heat exchanger section 91 reaches the point X 'more enthalpy. The liquid then passes through the expansion valve 69 and expands at a point γ to become biphasic. · The refrigerant then passes through the evaporator and absorbs heat to evaporate to reach the point Z. Then the steam enters the compressor through the ducts 30, 36 and 33 at its prescribed inlet. The heat exchanger embodiment of FIG. 13 can be used to switch the valves 28, 65 for -17- Ping () Λ4 specifications (210X297) (please read the notes on the back before filling out this page)-· -Order five, invention description (l5) A7 B7 heating and can be clearly seen in Figures 10 and 12 彳The formula is combined with other arguments of the present invention. Myba describes the invention from the point of view that it is operated as a cold relieving agent. However, the first argument of the present invention is equally applicable to non-irritating (zeotropic) refrigerants having two or more components. I have described the invention in terms of indoor and outdoor parts, but the main coils can of course have other similar relationships. It has been described that the present invention utilizes an expansion valve, but other expansion devices such as capillaries can be utilized whenever appropriate in the scope of the present invention. The present invention can be used with a variable speed compressor to improve capacity and / or efficiency between heating and cooling operations. The embodiments of Figs. 10 '12 and 13 can use a plurality of expansion devices and bypasses in front of the four-way valve as shown in a conventional manner so as to cause the refrigerant to expand just before entering a coil. All of the foregoing are inconsistent with the present invention. 18- The paper size is in accordance with the Chinese National Standard (CNS) Λ4 specification (2 丨 〇χ297mm) (#Please read the notes on the back before filling in this page) 袈. 、 1Τ